US9506531B2 - Multi-stage power-shift transmission - Google Patents

Multi-stage power-shift transmission Download PDF

Info

Publication number
US9506531B2
US9506531B2 US14/396,092 US201314396092A US9506531B2 US 9506531 B2 US9506531 B2 US 9506531B2 US 201314396092 A US201314396092 A US 201314396092A US 9506531 B2 US9506531 B2 US 9506531B2
Authority
US
United States
Prior art keywords
gear
spur
connection element
stage
shift
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related, expires
Application number
US14/396,092
Other languages
English (en)
Other versions
US20150080164A1 (en
Inventor
Stefan Beck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Assigned to ZF FRIEDRICHSHAFEN AG reassignment ZF FRIEDRICHSHAFEN AG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BECK, STEFAN
Publication of US20150080164A1 publication Critical patent/US20150080164A1/en
Application granted granted Critical
Publication of US9506531B2 publication Critical patent/US9506531B2/en
Expired - Fee Related legal-status Critical Current
Adjusted expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means

Definitions

  • the present invention relates to a power-shiftable multi-stage transmission in planetary design for a vehicle, which can be used as an automatic transmission, for example.
  • Power-shiftable multi-stage transmissions are used as vehicle transmissions in drive trains of vehicles.
  • Such multi-stage transmissions comprise a plurality of gear stages and a plurality of shift elements. Embodiments thereof exist for passenger vehicles having up to eight forward gears for front transverse installation or for longitudinal installation.
  • Power-shiftable multi-stage transmissions having spur-gear stages and planetary gear stages are provided for implementing the transmission ratios.
  • Multi-stage transmissions having planetary gear stages are usually automatic transmissions, which are shifted by means of friction elements or shift elements, such as clutches and brakes, for example.
  • Such multi-stage transmissions are usually connected to a start-up element, such as a hydrodynamic torque converter or a fluid coupling. Such a start-up element is subjected to a slip effect and is selectively provided with a lock-up clutch.
  • the known transmission concepts have specific advantages and specific disadvantages, and so these are interesting only for certain applications.
  • the patent document U.S. Pat. No. 7,819,772 B2 discloses a power-shiftable multi-stage transmission between a drive shaft and an output shaft.
  • the multi-stage transmission comprises a plurality of gear stages and a plurality of shift elements.
  • the present invention provides an improved power-shiftable multi-stage transmission in planetary design for a vehicle.
  • Advantageous embodiments will become apparent from the description that follows.
  • a power-shiftable multi-stage transmission in planetary design between a drive shaft and an output shaft in particular an automatic transmission for a vehicle, comprises two parallel shaft sections, six shift elements, at least two spur-gear stages and three planetary gear sets, each of which has one sun gear, one ring gear, and one planet carrier having a plurality of planetary gears, wherein the planet carrier is united in a carrier.
  • the two shaft sections can be connected to one another via the at least two spur-gear stages.
  • Different transmission ratios between the drive shaft and the output shaft can be implemented by means of a selective engagement of the six shift elements.
  • a plurality of forward gears, in particular at least nine forward gears, and at least one reverse gear can be implemented.
  • the vehicle can be a motor vehicle, for example a passenger vehicle, a truck, or any type of commercial vehicle.
  • the vehicle can be equipped with an internal combustion engine and, simultaneously or alternatively, with an electric drive, that is to say, the vehicle can also be embodied as a hybrid vehicle.
  • the splitting of the coupled planetary gear stages to only two shaft sections results in a short overall length and a compact overall arrangement.
  • a shift element can be a clutch or a brake, depending on the embodiment.
  • a shift element can be embodied either as a friction-locking shift element or as a form-locking shift element.
  • a shift element that is used can be embodied as a power-shifting clutch or a power-shifting brake.
  • a shift element can be embodied as a force-locking clutch or a force-locking brake, such as a multi-disk clutch, a band brake, or a cone clutch, for example.
  • a shift element can be embodied as a form-locking brake or a form-locking clutch, such as a synchronizing mechanism or a claw clutch, for example.
  • Different types of shift elements can be used for the six shift elements of the multi-stage transmission.
  • the multi-stage transmission can comprise exactly two spur-gear stages, that is, no more than two spur-gear stages, or exactly three spur-gear stages, that is, no more than three spur-gear stages.
  • the multi-stage transmission can comprise, for example, exactly three planetary gear sets, that is, no more than three planetary gear sets.
  • the multi-stage transmission advantageously has a short axial design, which is ideal for the front transverse design.
  • the multi-stage transmission is furthermore characterized by a relatively simple design, low costs and low weight, and a good transmission ratio range, low absolute rotational speeds, low relative rotational speeds, low planetary set torques and low shift element torques, good gearing efficiencies, and a compact design.
  • the multi-stage transmission is a 9-speed planetary power-shift transmission.
  • the multi-stage transmission can also be used as a front transverse system by arranging the gear sets and the shift elements in a suitable manner.
  • the multi-stage transmission can comprise at least nine forward gears.
  • the multi-stage transmission can be embodied with three planetary gear sets.
  • the power-shiftable multi-stage transmission in planetary design can therefore have at least nine forward gears and one reverse gear, as well as a gear ratio that is very well suited for motor vehicles and has a high overall gear ratio spread and favorable step changes.
  • the transmission can implement a high start-up gear ratio in the forward direction and can contain a direct gear.
  • the multi-stage transmission has a relatively simple design and is characterized, in particular, by a low number of shift elements, and eliminates double shifts when shifting sequentially. As a result, when shifting is implemented in defined groups of gears, it is possible in each case to disengage only one previously engaged shift element and engage one previously disengaged shift element.
  • first and second main systems two basic arrangements can be implemented, which are referred to in the following as the first and second main systems.
  • the three planetary gear sets are disposed on the first shaft section.
  • the second main system two of the three planetary gear sets are disposed on the first shaft section and one of the three planetary gear sets is disposed on the second shaft section, wherein one additional spur-gear stage is required as compared to the first main system.
  • shift elements in one power path of the transmission can be disposed in an equally acting manner at different points of the power path.
  • various possibilities for coupling to the different shafts of the multi-stage transmission result for the shift elements referred to in the following as the first and fourth shift elements.
  • An entire family of transmissions can be obtained as a result.
  • Embodiments of the first main system are described in the following.
  • the three planetary gear sets and the drive shaft can be disposed on a first shaft section of the two parallel shaft sections.
  • the output shaft can be disposed on a second shaft section of the two parallel shaft sections.
  • the two parallel shaft sections can be connected to one another via the two spur-gear stages.
  • a sun gear of a second planetary gear set of the three planetary gear sets and the drive shaft can be connected to one another in a rotationally fixed manner and form a first connection element.
  • a ring gear of a third planetary gear set of the three planetary gear sets and the carrier of the second planetary gear set can be connected to one another in a rotationally fixed manner and form a third connection element.
  • a sun gear of a first planetary gear set of the three planetary gear sets, a first spur gear of a second spur-gear stage of the at least two spur-gear stages, and a ring gear of the second planetary gear set can be connected to one another via a second, fourth, and fourteenth connection element.
  • the second, fourth, and fourteenth connection elements can have a common connection point.
  • the second connection element can be connected to the sun gear of the first planetary gear set.
  • the fourth connection element can be connected to the ring gear of the second planetary gear set.
  • the fourteenth connection element can be connected to the first spur gear of the second spur-gear stage.
  • a first spur gear of a first spur-gear stage of the at least two spur-gear stages and a ring gear of the first planetary gear set can be connected to one another and form a fifth connection element.
  • a second spur gear of the first spur-gear stage and the output shaft can be connected to one another and form a sixth connection element.
  • a carrier of the first planetary gear set and the output shaft can be connected to one another and form a seventh connection element.
  • a second spur gear of the second spur-gear stage and the output shaft can be connected to one another and form an eighth connection element.
  • a second shift element of the six shift elements can be disposed in the power flow between the drive shaft and a carrier of the third planetary gear set.
  • a third shift element of the six shift elements can be disposed in the power flow between the fourth connection element and the carrier of the third planetary gear set.
  • a fifth shift element of the six shift elements can be disposed in the power flow between the carrier of the third planetary gear set and a transmission housing.
  • a sixth shift element of the six shift elements can be disposed in the power flow between the sun gear of the third planetary gear set and the transmission housing.
  • the expression “in the power flow” means that a force can be transferred via the respective shift element if the respective shift element is engaged. If the shift element is disengaged, however, force cannot be transferred via the respective shift element and the power flow can therefore be interrupted.
  • a connection element can be a shaft.
  • a connection element can be either a rigid element or an element formed of at least two sub-elements coupled via a clutch. Therefore, two elements connected by means of one connection element can be connected to one another in a rotationally fixed manner and, for example, form a rigid shaft.
  • a connection element can comprise a clutch.
  • a freewheel to the housing or to another shaft can be disposed on each shaft of the multi-stage transmission.
  • some of the shift elements can be disposed at different points of the power path without this resulting in a change in the transmission ratios or a shift matrix.
  • power paths in the transmission can be connected or disconnected at different points via clutches, namely the first and fourth shift elements in this case, wherein this can take place in an equally acting manner at various points of a power path.
  • the seventh connection element can comprise a first shift element of the six shift elements.
  • the first shift element can be disposed in the power flow between the drive shaft and the carrier of the first planetary gear set.
  • the second connection element can comprise the first shift element.
  • the first shift element can be disposed in the power flow between the common connection point of the second, fourth, and fourteenth connection elements and the sun gear of the first planetary gear set.
  • the fifth connection element can comprise the first shift element.
  • the first shift element can be disposed in the power flow between a ring gear of the first planetary gear set and a first spur gear of the first spur-gear stage.
  • the sixth connection element can comprise the first shift element.
  • the first shift element can be disposed in the power flow between a second spur gear of the first spur-gear stage and the output shaft.
  • Embodiments of the second main system are described in the following.
  • one of the planetary gear sets can be disposed on the second shaft section.
  • the planetary gear set disposed on the second shaft section can be coupled in at least two different manners to the spur-gear stages while retaining the level of the stationary transmission ratios and the level of the transmission ratios of the main system.
  • two planetary gear sets and the drive shaft can be disposed on a first shaft section of the two parallel shaft sections.
  • a first planetary gear set of the three planetary gear sets and the output shaft can be disposed on a second shaft section of the two parallel shaft sections.
  • the two parallel shaft sections can be connected to one another via three spur-gear stages.
  • a sun gear of a second planetary gear set of the three planetary gear sets and the drive shaft can be connected to one another in a rotationally fixed manner and form a first connection element.
  • a ring gear of a third planetary gear set of the three planetary gear sets and the carrier of the second planetary gear set can be connected to one another in a rotationally fixed manner and form a third connection element.
  • a ring gear of the second planetary gear set and a first spur gear of a second spur-gear stage of the at least two spur-gear stages can be connected to one another and form a fourth connection element.
  • a second spur gear of the second spur-gear stage and the output shaft can be connected and form an eighth connection element.
  • the first spur gear of the second spur-gear stage, a first spur gear of a fourth spur-gear stage of the at least two spur-gear stages, and the fourth connection element can be connected to one another, wherein the connection between the first spur gear of the fourth spur-gear stage of the at least two spur-gear stages and the fourth connection element form a ninth connection element, and the connection between the first spur gear of the second spur-gear stage and the fourth and ninth connection elements form a fourteenth connection element.
  • the output shaft and the ring gear of the first planetary gear set can be connected and form a tenth connection element.
  • a first spur gear of a third spur-gear stage of the at least two spur-gear stages and the drive shaft can be connected to one another and form a thirteenth connection element.
  • the drive shaft can be connected to the carrier of the third planetary gear set by means of a second shift element of the six shift elements.
  • the carrier of the third planetary gear set having the connection of the first spur gear of the second spur-gear stage can be connected to the ring gear of the second planetary gear set by means of a third shift element of the six shift elements.
  • a fifth shift element of the six shift elements can be disposed in the power flow between the carrier of the third planetary gear set and the transmission housing.
  • a sixth shift element of the six shift elements can be disposed in the power flow between the sun gear of the third planetary gear set and the transmission housing.
  • a second spur gear of the fourth spur-gear stage and the carrier of the first planetary gear set can be connected and form an eleventh connection element.
  • a second spur gear of the third spur-gear stage and the sun gear of the first planetary gear set can be connected and form a twelfth connection element.
  • two planetary gear sets and the drive shaft can be disposed on a first shaft section of the two parallel shaft sections.
  • a first planetary gear set of the three planetary gear sets and the output shaft can be disposed on a second shaft section of the two parallel shaft sections.
  • the two parallel shaft sections can be connected to one another via three spur-gear stages.
  • a sun gear of a second planetary gear set of the three planetary gear sets and the drive shaft can be connected to one another in a rotationally fixed manner and form a first connection element.
  • a ring gear of a third planetary gear set of the three planetary gear sets and the carrier of the second planetary gear set can be connected to one another in a rotationally fixed manner and form a third connection element.
  • a ring gear of the second planetary gear set and a first spur gear of a second spur-gear stage of the at least two spur-gear stages can be connected to one another and form a fourth connection element.
  • a second spur gear of the second spur-gear stage and the output shaft can be connected and form an eighth connection element.
  • the carrier of the second planetary gear set and a first spur gear of a fourth spur-gear stage of the at least two spur-gear stages can be connected in a rotationally fixed manner and form a ninth connection element.
  • the output shaft and the ring gear of the first planetary gear set can be connected in a rotationally fixed manner and form a tenth connection element.
  • a first spur gear of a third spur-gear stage of the at least two spur-gear stages and the drive shaft can be connected and form a thirteenth connection element.
  • the drive shaft can be connected to the carrier of the third planetary gear set by means of a second shift element of the six shift elements.
  • the carrier of the third planetary gear set having the connection of the first spur gear of the second spur-gear stage can be connected to the ring gear of the second planetary gear set by means of a third shift element of the six shift elements.
  • a fifth shift element of the six shift elements can be disposed in the power flow between the carrier of the third planetary gear set and the transmission housing.
  • a sixth shift element of the six shift elements can be disposed in the power flow between the sun gear of the third planetary gear set and the transmission housing.
  • a second spur gear of the fourth spur-gear stage and the sun gear of the first planetary gear set can be connected and form an eleventh connection element.
  • a second spur gear of the third spur-gear stage and the carrier of the first planetary gear set can be connected and form a twelfth connection element.
  • first shift element can be positioned in an equally acting manner at at least five locations and the fourth shift element can be positioned in an equally acting manner at at least two locations.
  • the thirteenth connection element can therefore comprise a first shift element of the six shift elements.
  • the first shift element can be disposed in the power flow between the drive shaft and the spur gear of the third spur-gear stage.
  • the twelfth connection element can comprise a first shift element of the six shift elements.
  • the eleventh connection element can comprise a first shift element of the six shift elements.
  • the tenth connection element can comprise a first shift element of the six shift elements.
  • the ninth connection element can comprise a first shift element.
  • the eighth connection element can comprise a fourth shift element of the six shift elements.
  • the fourth shift element can be disposed in the power flow between the second spur gear of the second spur-gear stage and the output shaft.
  • the fourteenth connection element can comprise a fourth shift element of the six shift elements.
  • the fourteenth shift element can be disposed in the power flow between the fourth connection element or the ninth connection element and the first spur gear of the second spur-gear stage.
  • a power source can be disposed on the drive shaft.
  • the power source can be a motor, for example an electric motor.
  • the power source can be disposed axially parallel to the drive shaft.
  • the power source can be disposed directly on the drive shaft.
  • a further advantage of the multi-stage transmission presented here is that an electric machine can be additionally attached to each shaft as a generator and/or as an additional drive motor.
  • an electric machine or any other type of force/power supply can be disposed, in principle, on each shaft, which is also referred to as a connection element in this case.
  • a connection to the drive shaft appears to make sense for the electric machine in particular, however.
  • the electric machine can be connected to the drive shaft either directly or in an axially parallel manner via a pair of gears.
  • all three planetary gear sets are designed, for example, as so-called minus planetary gear sets, the respective ring gears of which rotate, with the carrier held, in the direction counter to the sun gear.
  • At least one planetary gear set can be designed as a so-called plus planetary gear set if the above-described carrier and ring gear connection of the planetary gear set in question is exchanged and the stationary transmission ratio is adjusted.
  • a plus planetary gear set is a planetary transmission in which the ring gear rotates in the same direction of rotation as the sun gear when the carrier is held.
  • a minus planetary gear set comprises planetary gears, which are rotatably mounted on a planet carrier and mesh with the sun gear and ring gear of this planetary gear set such that, with the planet carrier held and the sun gear rotating, the ring gear rotates in the direction of rotation counter to that of the sun gear.
  • a plus planetary gear set comprises inner and outer planetary gears, which are rotatably mounted on a planet carrier and are in tooth engagement with one another, wherein the sun gear of this planetary gear set meshes with the aforementioned inner planetary gears, and the ring gear of this planetary gear set meshes with the aforementioned outer planetary gears such that, with the planet carrier held and the sun gear rotating, the ring gear rotates in the same direction of rotation as the sun gear.
  • a point that applies in general for all the different embodiments is that, wherever a connection allows for it, individual, or a plurality of, minus planetary gear sets can be converted to plus planetary gear sets if the carrier and ring gear connection is simultaneously exchanged and the value of the stationary transmission ratio is increased by one.
  • the first forward gear of the multi-stage transmission can be implemented by engaging the third, fourth, and sixth shift elements.
  • the second forward gear can be implemented by engaging the second, third, and fourth shift elements.
  • the third forward gear can be implemented by engaging the second, fourth, and sixth shift elements.
  • the fourth forward gear can be implemented by engaging the first, second, and fourth shift elements.
  • the fifth forward gear can be implemented by engaging the first, second, and sixth shift elements.
  • the sixth forward gear can be implemented by engaging the first, second, and third shift elements.
  • the seventh forward gear can be implemented by engaging the first, third, and sixth shift elements.
  • the eighth forward gear can be implemented by engaging the first, third, and fifth shift elements.
  • the ninth forward gear can be implemented by engaging the first, fifth, and sixth shift elements.
  • the reverse gear can be implemented by engaging the fourth, fifth, and sixth shift elements.
  • the transmission described can comprise the drive-side first shaft section and the output-side second shaft section. These two shaft sections can be connected by at least two power paths, to which the at least two spur-gear stages can belong. If power paths are disconnected by means of clutches, this can take place in an equivalent manner at any location within the power path. If such power paths can be connected to the transmission housing by means of brakes, this brake can also engage in an equivalent manner at other locations in the power path. Identical stationary transmission ratios can be obtained by means of different planetary transmission designs, which should be considered equivalent within the meaning of this invention.
  • FIG. 1 shows a schematic depiction of a vehicle comprising a power-shiftable multi-stage transmission according to one example embodiment of the present invention:
  • FIG. 2 shows a gear pattern of a 9-speed multi-stage transmission according to one example embodiment of the present invention
  • FIG. 3 shows a shift pattern, as an example, of a multi-stage transmission according to one example embodiment of the present invention
  • FIG. 4 shows variant embodiments of a first main system of a multi-stage transmission according to one example embodiment of the present invention
  • FIGS. 5 to 8 show schematic depictions of the first main system according to example embodiments of the present invention.
  • FIG. 9 shows a depiction of a second main system according to one example embodiment of the present invention.
  • FIG. 10 shows variant embodiments of the second main system of a multi-stage transmission according to one example embodiment of the present invention
  • FIG. 11 shows a gear pattern of the second main system according to a further example embodiment of the present invention.
  • FIG. 12 shows a schematic depiction of the first main system comprising a power source, according to one example embodiment of the present invention.
  • FIG. 13 shows a schematic depiction of a multi-stage transmission comprising a power source, according to one example embodiment of the present invention.
  • FIG. 1 An overview of the use of a power-shiftable multi-stage transmission is presented in the following with reference to FIG. 1 .
  • a first main system of a power-shiftable multi-stage transmission will then be presented in FIG. 2 as an example embodiment of the present invention and will be subsequently described in different variant interlockings with reference to FIGS. 4 to 8 .
  • a second main system of a power-shiftable multi-stage transmission and different variant embodiments and interlockings thereof are depicted in FIGS. 9 to 11 .
  • FIGS. 12 and 13 show a hybridization of a power-shiftable multi-stage transmission using the first main system as an example.
  • FIG. 3 shows a shift matrix for a power-shiftable multi-stage transmission according to the invention.
  • FIG. 1 shows a schematic depiction of a vehicle 100 comprising an engine 110 and a power-shiftable multi-stage transmission 120 in planetary design, according to one example embodiment of the present invention.
  • the power-shiftable multi-stage transmission 120 which is also referred to as a planetary power-shift transmission or a power-shift unit, is installed in the vehicle 100 in a front transverse installation in this example embodiment.
  • the engine 110 for example an internal combustion engine, is connected to the power-shiftable multi-stage transmission 120 by means of a drive shaft AN.
  • An output shaft AB of the power-shiftable multi-stage transmission 120 connects the power-shiftable multi-stage transmission 120 to the front axle of the vehicle 100 , in order to drive the vehicle 100 .
  • the power-shiftable multi-stage transmission 120 comprises three planetary gear sets, two or three spur-gear stages, and six shift elements, of which four are clutches and two are brakes, wherein two shift elements must be engaged simultaneously.
  • the power-shiftable multi-stage transmission 120 does not comprise any fixed housing clutches and can shift nine forward gears and one reverse gear.
  • the start-up element can be a hydrodynamic torque converter, a hydrodynamic clutch, an additional start-up clutch, an integrated start-up clutch or brake, an additional electric machine, or a power shuttle unit or a power-reversing unit.
  • FIG. 2 shows a gear pattern of a power-shiftable multi-stage transmission 120 according to one example embodiment of the present invention.
  • the example embodiment shows an embodiment of a multi-stage transmission 120 that is referred to as the first main system.
  • the power-shiftable multi-stage transmission 120 can be the multi-stage transmission 120 shown with reference to FIG. 1 .
  • the multi-stage transmission 120 which is also referred to as a planetary power-shift transmission, is embodied as a 9-speed multi-stage transmission according to this example embodiment.
  • the multi-stage transmission 120 comprises two parallel shaft sections WS 1 , WS 2 , six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 , two spur-gear stages STS 1 , STS 2 , and three planetary gear sets PS 1 , PS 2 , PS 3 , all of which are disposed in a housing GG of the multi-stage transmission 120 .
  • all three planetary gear sets PS 1 , PS 2 , PS 3 are embodied as simple minus planetary gear sets, the respective ring gears HO 1 , HO 2 , HO 3 of which rotate, with the carrier ST 1 , ST 2 , ST 3 held, in the direction counter to the sun gear SO 1 , SO 2 , SO 3 .
  • a minus planetary gear set comprises planetary gears, which are rotatably mounted on a planet carrier and mesh with the sun gear and the ring gear of this planetary gear set.
  • the three planetary gear sets PS 1 , PS 2 , PS 3 are disposed in the axial direction coaxially and successively in the sequence “PS 1 , PS 2 , PS 3 ” on the first shaft section WS 1 of the two parallel shaft sections WS 1 , WS 2 .
  • a first spur gear ST 1 a of a first spur-gear stage STS 1 of the two spur-gear stages STS 1 , STS 2 and a first spur gear ST 2 a of a second spur-gear stage STS 2 of the two spur-gear stages STS 1 , STS 2 are disposed coaxially and successively on the first shaft section WS 1 between the first planetary gear set PS 1 and the second planetary gear set PS 2 .
  • the drive shaft AN is disposed on the first shaft section WS 1
  • the output shaft AB is disposed on a second shaft section WS 2 of the two parallel shaft sections WS 1 , WS 2 .
  • the two shaft sections WS 1 WS 2 are connected to one another via the two spur-gear stages STS 1 , STS 2 .
  • the shift elements K 1 , K 2 , K 3 , K 4 are designed as clutches and the two shift elements B 1 , B 2 are designed as brakes and are also referred to as such in the following.
  • Different transmission ratios between the drive shaft AN and the output shaft AB can be implemented by means of a selective engagement of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 . At least nine forward gears and at least one reverse gear can be implemented in this manner.
  • a coupling of the individual elements of the three planetary gear sets PS 1 , PS 2 , PS 3 to one another, to the two spur-gear stages STS 1 , STS 2 , and to the drive shaft AN and to the output shaft AB are described in the following.
  • the multi-stage transmission 120 comprises at least nine connection elements, which are labeled 1 to 8 and 14 .
  • the connection elements 1 , 2 , 3 , 4 , 5 , 6 , 7 , 8 , 14 can be designed as shafts, wherein one or more shift elements can be disposed within the connection elements 1 , 2 , 3 , 4 , 5 , 6 , 7 , 8 , 14 in each case, as described in more detail in the following.
  • a sun gear SO 2 of a second planetary gear set PS 2 of the three planetary gear sets PS 1 , PS 2 , PS 3 and the drive shaft AN are connected to one another in a rotationally fixed manner and form a first connection element 1 .
  • a sun gear SO 1 of a first planetary gear set PS 1 of the three planetary gear sets PS 1 , PS 2 , PS 3 , a spur gear STS 2 a of a second spur-gear stage STS 2 , and a ring gear HO 2 of the second planetary gear set PS 2 are connected to one another via a second, a fourth, and a fourteenth connection element 2 , 4 , 14 .
  • the second, fourth, and fourteenth connection elements 2 , 4 , 14 have a common connection point.
  • the second connection element 2 is connected to the sun gear SO 1 of the first planetary gear set PS 1 .
  • the fourth connection element 4 is connected to the ring gear HO 2 of the second planetary gear set PS 2 .
  • the fourteenth connection element 14 is connected to the first spur gear ST 2 a of the second spur-gear stage STS 2 .
  • a ring gear HO 3 of a third planetary gear set PS 3 of the three planetary gear sets PS 1 , PS 2 , PS 3 and the carrier ST 2 of the second planetary gear set PS 2 are connected to one another in a rotationally fixed manner and form a third connection element.
  • the second connection element 2 and the fourth connection element 4 are connected to one another such that a connection also exists between the ring gear HO 2 of the second planetary gear set PS 2 and the sun gear SO 1 of the first planetary gear set PS 1 .
  • the first spur gear ST 1 a of the first spur-gear stage STS 1 is connected to a ring gear HO 1 of the first planetary gear set PS 1 and forms a fifth connection element 5 .
  • a second spur gear ST 1 b of the first spur-gear stage STS 1 and the output shaft AB are connected and form a sixth connection element 6 .
  • a carrier ST 1 of the first planetary gear set PS 1 is connected to the drive shaft AN and forms a seventh connection element 7 .
  • a second spur gear ST 2 b of the second spur-gear stage STS 2 and the output shaft AB are connected and form an eighth connection element 8 .
  • the seventh connection element 7 comprises a first shift element K 1 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 , wherein the first shift element K 1 is disposed in the power flow between the drive shaft AN and the carrier ST 1 of the first planetary gear set PS 1 .
  • a second shift element K 2 of the six shift elements K 1 K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the drive shaft AN and a carrier ST 3 of the third planetary gear set PS 3 .
  • a third shift element K 3 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the rotationally fixed connection of the ring gear HO 2 of the second planetary gear set PS 2 to the spur gear ST 2 a of the second spur-gear stage STS 2 and the carrier ST 3 of the third planetary gear set PS 3 .
  • the eighth connection element 8 comprises a fourth shift element K 4 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 , wherein the fourth shift element K 4 is disposed in the power flow between the second spur gear ST 2 b of the second spur-gear stage STS 2 and the output shaft AB.
  • a fifth shift element B 1 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the carrier ST 3 of the third planetary gear set PS 3 and a transmission housing GG.
  • a sixth shift element B 2 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the sun gear SO 3 of the third planetary gear set PS 3 and the transmission housing GG.
  • the first connection element 1 of the multi-stage transmission 120 extends, in sections, so as to be centered between the second connection element 2 and the fourth connection element 4 .
  • the seventh connection element engages around the drive shaft AN or the first connection element 1 in the axial direction via the first shift element K 1 .
  • the second shift element K 2 engages completely around the third connection element 3 in the axial direction.
  • the first spur gear ST 1 a of the first spur-gear stage is disposed radially above the first planetary gear set PS 1 .
  • the fifth shift element B 1 and the sixth shift element B 2 are disposed, from a spatial perspective, directly axially adjacent to one another in a region outside the sequence “PS 1 /ST 1 a , ST 2 a , PS 2 , PS 3 ” next to the third planetary gear set PS 3 .
  • the fifth shift element B 1 is disposed between the third planetary gear set PS 3 and the sixth shift element B 2 .
  • the fifth and the sixth shift elements B 1 , B 2 are connected to the transmission housing GG.
  • the kinematic connection of the fifth and sixth shift elements B 1 , B 2 to the third planetary gear set PS 3 requires that the shift element B 1 be disposed closer to the third planetary gear set PS 3 than the shift element B 2 .
  • the spatial arrangement of the shift elements B 1 , B 2 depicted in FIG. 2 shall be construed only as an example.
  • the shift element B 1 can also be disposed at least partially radially above the shift element B 2 or, as an alternative, the sixth shift element B 2 can be disposed in the region of the rotational axis of the first shaft section WS 1 .
  • the third shift element K 3 is disposed axially directly next to the fifth shift element B 1 .
  • the third connection element 3 , the second shift element K 2 , and the third planetary gear set PS 3 engage completely around the connection of the ring gear HO 2 of the second planetary gear set PS 2 to the third shift element K 3 , in the axial direction.
  • the spatial arrangement of the two spur gears ST 1 b , ST 2 b of the two spur-gear stages STS 1 , STS 2 on the second shaft section WS 2 is in the form “ST 1 b , ST 2 b ” as viewed in the axial direction.
  • the fourth shift element K 4 is directly and axially adjacent to the second spur gear ST 2 b of the second spur-gear stage STS 2 .
  • the first four shift elements K 1 , K 2 , K 3 , K 4 are designed as lamellar clutches that can be engaged in a friction-locking manner, which naturally can be implemented as claw clutches or cone clutches that can be engaged in a form-locking manner in another example embodiment.
  • the shift elements B 1 , B 2 designed as brakes are implemented as multi-disk brakes that can be engaged in a friction-locking manner, which naturally can also be implemented as band brakes that can be engaged in a friction-locking manner, or as claw brakes or cone brakes that can be engaged in a form-locking manner in other example embodiments.
  • a plurality of functionally identical, variant transmissions can be derived from the transmission 120 depicted in FIG. 2 .
  • the clutch K 1 of the main system shown in FIG. 2 can be disposed in three other positions, which function in an identical manner.
  • the clutch K 4 can be disposed in one other position. This is explained in detail in FIG. 4 , which follows.
  • FIG. 3 shows a shift pattern, as an example, of a multi-stage transmission according to one example embodiment of the present invention.
  • the multi-stage transmission or the planetary power-shift transmission can be one of the multi-stage transmissions described in the preceding or in the following.
  • gear steps representing one gear of the multi-stage transmission in each case are listed in the first column of the table shown in FIG. 3 .
  • An “x” is entered for each engaged shift element B 1 , B 2 , K 1 , K 2 , K 3 , K 4 in the next six columns, which are reserved for the six shift elements B 1 , B 2 , K 1 , K 2 , K 3 , K 4 , which were previously described with reference to FIG. 2 , for example.
  • the two brakes B 1 and B 2 are listed first, followed by the four clutches K 1 , K 2 , K 3 , K 4 .
  • a shift element B 1 , B 2 , K 1 , K 2 , K 3 , K 4 force is transferred via the respective shift element B 1 , B 2 , K 1 , K 2 , K 3 , K 4 .
  • the respective shift element B 1 , B 2 , K 1 , K 2 , K 3 , K 4 can be a rigid connection element.
  • the second-to-last column shows a transmission ratio i, as an example, followed by a resultant gear step ⁇ in the last column.
  • the engaged shift elements which are indicated with an “x”, can also be referred to by the English language expression “engaged shifting elements”.
  • example values for the respective transmission ratios i of the individual gear steps and the step changes ⁇ to be determined therefrom are also presented in the shift matrix.
  • the transmission ratios presented result from the (typical) stationary transmission ratios of the three planetary gear sets PS 1 , PS 2 , PS 3 of minus 1.600 for the first planetary gear set PS 1 , minus 1.600 for the second planetary gear set PS 2 , and minus 3.642 for the third planetary gear set and for the first spur-gear stage STS 1 of 1.000 and for the second spur-gear stage STS 2 of 3.228.
  • the stationary transmission ratios of the spur-gear stages in this case can be changed within a design-related tolerance range without this substantially affecting the transmission ratios.
  • the shift matrix shows that double shifts or group shifts are eliminated when shifting sequentially.
  • Two adjacent gear steps use two of the necessary three shift elements.
  • the sixth gear is preferably implemented as a direct gear.
  • the transmission ratios presented and the variables derived therefrom represent a preferred embodiment. A person skilled in the art may also use other values here, in accordance with the requirements on the multi-stage transmission.
  • the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 comprise the four clutches K 1 , K 2 , K 3 , K 4 and the two brakes B 1 , B 2 .
  • the first four shift elements K 1 , K 2 , K 3 , K 4 are referred to as clutches K 1 , K 2 , K 3 , K 4
  • the fifth and sixth shift elements B 1 , B 2 are referred to as brakes B 1 , B 2 .
  • the first forward gear is implemented by engaging the brake B 2 and the clutches K 3 , K 4
  • the second forward gear is implemented by engaging the clutches K 2 , K 3 , K 4
  • the third forward gear is implemented by engaging the brake B 2 and the clutches K 2 , K 4
  • the fourth forward gear is implemented by engaging the clutches K 1 , K 2 , K 4
  • the fifth forward gear is implemented by engaging the brake B 2 and the clutches K 1 , K 2
  • the sixth forward gear is implemented by engaging the clutches K 1 , K 2 , K 3
  • the seventh forward gear is implemented by engaging the brake B 2 and the clutches K 1 , K 3
  • the eighth forward gear is implemented by engaging the brake B 1 and the two clutches K 1 , K 3
  • the ninth forward gear is implemented by engaging the two brakes B 1 , B 2 and the clutch K 1 .
  • the shift matrix in FIG. 3 also shows that the reverse gear is implemented by engaging the two brakes B 1 , B 2 and the
  • the transmission ratio i can also be referred to by the English language expression “ratio”.
  • a transmission ratio i of 5.171 is obtained
  • a transmission ratio i of 3.103 is obtained
  • a transmission ratio i of 2.191 is obtained
  • a transmission ratio i of 1.657 is obtained
  • a transmission ratio i of 1.234 is obtained
  • a direct transmission ratio i of 1.000 is obtained
  • for the seventh gear a transmission ratio i of 0.846 is obtained
  • for the eighth gear a transmission ratio i of 0.688 is obtained
  • a transmission ratio i of 0.575 is obtained.
  • the shift matrix also shows that a transmission ratio i of 4.965 is obtained for the reverse gear. Consequently, a gear increment ⁇ or “step” of 1.666 results from the first gear to the second gear, a gear increment ⁇ of 1.416 results from the second gear to the third gear, a gear increment ⁇ of 1.322 results from the third gear to the fourth gear, a gear increment ⁇ of 1.343 results from the fourth gear to the fifth gear, a gear increment ⁇ of 1.234 results from the fifth gear to the sixth gear, a gear increment ⁇ of 1.182 results from the sixth gear to the seventh gear, a gear increment ⁇ of 1.230 results from the seventh gear to the eighth gear, and a gear increment ⁇ of 1.197 results from the eighth gear to the ninth gear.
  • the transmission therefore has a spread of 8.993.
  • the ratio of the reverse gear to the first gear is minus 0.960 and is therefore very close to an ideal value of minus 1.
  • the multiple gears M 4 ′, M 4 ′′, M 4 ′′′ listed in the first column are additional shift combinations, which also represent the fourth gear.
  • the first multiple gear M 4 is implemented by engaging the brake B 1 and the clutches K 1 , K 4
  • the second multiple gear M 4 ′′ is implemented by engaging the clutches K 1 , K 3 , K 4
  • the third multiple gear M 4 ′′′ is implemented by engaging the brake B 2 and the clutches K 1 , K 4 .
  • the vehicle for example the vehicle shown in FIG. 1
  • a shift element integrated in the transmission can be started up with a shift element integrated in the transmission.
  • a shift element that is required in the first forward gear and in the reverse gear, namely the brake B 2 or the clutch K 4 in this case.
  • the clutch K 4 is also required in the second forward gear. If the clutch K 4 is used as the start-up element integrated in the transmission, it is therefore even possible to implement a start-up in the first four forward gears and the reverse gear.
  • preferred stationary transmission ratios of the main system are ⁇ 1.600 for the first planetary set PS 1 , ⁇ 1.600 for the second planetary set PS 2 , ⁇ 3.642 for the third planetary set PS 3 , and 1.00 for the spur-gear stage STS 1 (ST 1 a -ST 1 b ), 3.228 for the second spur-gear stage STS 2 (ST 2 a -ST 2 b ) and, for the variant embodiments having three spur-gear stages, as shown in FIGS.
  • Possible variant interlockings of the multi-stage transmission shown in FIG. 2 are depicted in the following and in FIGS. 4 to 8 .
  • Any spatial arrangement of the shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 of the example embodiment of a multi-stage transmission 120 depicted in FIG. 2 within the multi-stage transmission 120 is possible, in principle, and is limited only by the dimensions and the outer shape of the transmission housing GG.
  • variant component arrangements of the multi-stage transmission according to FIG. 2 are depicted in the following figures, wherein all the kinematic couplings of the planetary gear sets, spur-gear stages, shift elements and shafts, and connection elements among one another are copied, unchanged, from FIG. 2 .
  • FIG. 4 shows an overview of variant interlockings of the first main system of a multi-stage transmission 120 , which was previously described with reference to FIG. 2 , according to different example embodiments of the present invention
  • the gear pattern depicted in FIG. 4 corresponds to the gear pattern of a multi-stage transmission 120 depicted in FIG. 2 , from which a plurality of equally acting, variant transmissions can be derived, wherein three additional, equally acting, variant positions are shown for the first shift element K 1 , i.e., the clutch K 1 , and one other variant position is shown for the fourth shift element K 4 , i.e., the clutch K 4 .
  • the three variant positions for the clutch K 1 are labeled A 1 , A 2 , A 3 in FIG. 4 , and the variant position for the clutch K 4 is labeled A 4 .
  • a first variant position A 1 of the clutch K 1 the clutch K 1 is disposed on the second connection element 2 between the sun gear SO 1 of the first planetary gear set and the fourth connection element 4 .
  • the first shift element K 1 is disposed in the power flow between the ring gear HO 2 of the second planetary gear set PS 2 , the first spur gear ST 2 a of the second spur-gear stage STS 2 , and the sun gear SO 1 of the first planetary gear set PS 1 .
  • the clutch K 1 is disposed on the fifth connection element 5 between the ring gear HO 1 of the first planetary gear set and the first spur gear ST 1 a of the first spur-gear set STS 1 .
  • the first shift element K 1 is disposed in the power flow between a ring gear HO 1 of the first planetary gear set PS 1 and a first spur gear ST 1 a of the first spur-gear stage STS 1 .
  • the clutch K 1 is disposed on the sixth connection element 6 between the second spur gear ST 1 b of the first spur-gear stage STS 1 and the output shaft AB.
  • the first shift element K 1 is disposed in the power flow between a second spur gear ST 1 b of the first spur-gear stage STS 1 and the output shaft AB.
  • the fourth connection element 4 comprises the clutch K 4 .
  • the fourth shift element K 4 is disposed in the power flow between the ring gear HO 2 of the second planetary gear set PS 2 and the first spur gear ST 2 a of the second spur-gear stage STS 2 and the sun gear SO 1 of the first planetary gear set PS 1 .
  • the clutch K 4 in the variant position A 4 is disengaged, the first spur gear ST 2 a of the second spur-gear stage is decoupled from the connection of the sun gear SO 1 of the first planetary gear set PS 1 and the ring gear HO 2 of the second planetary gear set PS 2 .
  • the fourth shift element K 4 is disposed in the fourteenth connection element.
  • the seventh connection element 7 establishes a rotationally-fixed connection between the drive shaft AN and the carrier ST 1 of the first planetary gear set PS 1 , and the sun gear SO 1 of the first planetary gear set can be coupled to the carrier ST 2 of the second planetary gear set via the clutch K 1 .
  • All eight combinations of the position for the clutch K 1 depicted in FIG. 2 and the three variant positions A 1 , A 2 , A 3 for the clutch K 1 with the position for the clutch K 4 depicted in FIG. 2 and the variant position A 4 for the clutch K 4 are possible.
  • One of the possible variant positions A 1 , A 2 , A 3 , A 4 for the clutches K 1 and K 4 is shown in the FIGS. 5 to 8 , respectively, which follow.
  • FIG. 5 shows a schematic depiction of another example embodiment of the first main system of the multi-stage transmission 120 previously described with reference to FIG. 2 .
  • This shows the first variant position for the clutch K 1 , which is labeled A 1 in FIG. 4 .
  • the first spur-gear stage STS 1 was axially displaced together with the first planetary gear set PS 1 such that the clutch K 1 can be spatially disposed between the first planetary gear set PS 1 and the second spur-gear stage STS 2 .
  • the fourth clutch K 4 is disposed spatially differently as compared to the multi-stage transmission depicted in FIG. 2 , namely between the two spur-gear stages STS 1 , STS 2 .
  • the carrier ST 1 of the first planetary gear set PS 1 is connected in a rotationally fixed manner to the drive shaft AN, i.e., the first connection element 1 and, therefore, to the sun gear SO 2 of the second planetary gear set PS 2 .
  • the sun gear SO 1 of the first planetary gear set PS 1 and the ring gear HO 2 of the second planetary gear set PS 2 and the first spur gear ST 2 a of the second spur-gear stage STS 2 can be coupled to one another via the clutch K 1 .
  • the clutch K 4 is disposed between the second spur gear ST 1 b of the first spur-gear stage STS 1 and the second spur gear ST 2 b of the second spur-gear stage STS 2 .
  • FIG. 6 shows a schematic depiction of another example embodiment of the first main system of the multi-stage transmission 120 previously described with reference to FIG. 2 . This shows the second variant position for the clutch K 1 , which is labeled A 2 in FIG. 4 .
  • the first spur-gear stage STS 1 is axially displaced and is disposed on the opposite side of the first planetary gear set PS 1 relative to the second planetary gear set PS 2 . Due to the axial displacement of the first spur-gear stage STS 1 , the seventh connection element 7 extends so as to be centered within the fifth connection element 5 . The position of the fourth shift element K 4 corresponds to the variant position previously shown in FIG. 5 .
  • the drive shaft AN is connected in a rotationally fixed manner to the carrier ST 1 of the first planetary gear set PS 1 .
  • the sun gear SO 1 of the first planetary gear set PS 1 is connected in a rotationally fixed manner to the ring gear HO 2 of the second planetary gear set PS 2 .
  • the first spur gear ST 1 a of the first spur gear stage STS 1 can be coupled to the ring gear HO 1 of the first planetary gear set PS 1 via the first shift element K 1 .
  • FIG. 7 shows a schematic depiction of another example embodiment of the first main system of the multi-stage transmission 120 previously described with reference to FIG. 2 . This shows the third variant position for the clutch K 1 , which is labeled A 3 in FIG. 4 .
  • the second spur gear ST 1 b of the first spur-gear stage STS 1 can be coupled to the output shaft AB via the clutch K 1 .
  • the position of the first spur-gear stage STS 1 and the fourth clutch K 4 corresponds to the variant position previously shown in FIGS. 5 and 6 .
  • the clutch K 1 and the clutch K 4 are disposed next to one another, wherein a clutch element of the two clutches K 1 , K 4 is connected in a rotationally fixed manner to the output shaft AB.
  • the first spur gear ST 1 a of the first spur-gear stage STS 1 is connected in a rotationally fixed manner to the ring gear HO 1 of the first planetary gear set PS 1 .
  • FIG. 8 shows a schematic depiction of another example embodiment of the first main system of the multi-stage transmission 120 previously described with reference to FIG. 2 . This shows the variant position for the fourth clutch K 4 , which is labeled A 4 in FIG. 4 .
  • the clutch K 4 is disposed between the first spur gear ST 2 a of the second spur-gear stage STS 2 and the rotationally-fixed connection of the ring gear HO 2 of the second planetary gear set PS 2 and the sun gear SO 1 of the first planetary gear set PS 1 . Therefore, the first spur gear ST 2 a of the second spur-gear stage STS 2 and the ring gear HO 2 of the second planetary gear set PS 2 and the sun gear SO 1 of the first planetary gear set PS 1 can be coupled by means of the clutch K 4 .
  • the second spur gear ST 2 b of the second spur-gear stage STS 2 is connected to the output shaft AB in a rotationally fixed manner.
  • the power-shiftable multi-stage transmission 120 shown in FIGS. 2 and 4 to 8 can be implemented in an equally acting manner by disposing the first planetary gear set PS 1 on the output shaft AB.
  • FIGS. 9 to 11 show two variant embodiments and possible alternative variant interlockings of a multi-stage transmission 120 , according to the invention, which has a planetary gear set on the output shaft AB.
  • Such a multi-stage transmission 120 is referred to in the following as a second main system.
  • FIG. 9 shows a gear pattern of a power-shiftable multi-stage transmission 120 according to one example embodiment of the present invention.
  • the example embodiment is based on the aforementioned second main system of a multi-stage transmission 120 .
  • the power-shiftable multi-stage transmission 120 can be the multi-stage transmission 120 shown with reference to FIG. 1 .
  • the multi-stage transmission 120 which is also referred to as a planetary power-shift transmission, is embodied as a 9-speed multi-stage transmission according to this example embodiment.
  • the multi-stage transmission 120 shown in FIG. 9 does not comprise a first spur-gear stage STS 1 , although this does comprise the second spur-gear stage STS 2 previously described with reference to FIG. 2 , as well as two additional spur-gear stages STS 3 , STS 4 .
  • Three spur-gear stages STS 2 , STS 3 , STS 4 are therefore used in this case, instead of two spur-gear stages STS 1 , STS 2 , as shown in FIG. 2 , for example, for the first main system.
  • the first planetary gear set PS 1 is positioned on the output shaft AB.
  • the multi-stage transmission 120 shown in FIG. 9 comprises two parallel shaft sections WS 1 , WS 2 , six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 , three spur-gear stages STS 2 , STS 3 , STS 4 and three planetary gear sets PS 1 , PS 2 , PS 3 , all of which are disposed in a housing GG of the planetary power-shift transmission 120 .
  • all three planetary gear sets PS 1 , PS 2 , PS 3 are embodied as simple minus planetary gear sets, the respective ring gears HO 1 , HO 2 , HO 3 of which rotate, with the carrier ST 1 , ST 2 , ST 3 held, in the direction counter to the sun gear SO 1 , SO 2 , SO 3 .
  • the second and third planetary gear sets PS 2 , PS 3 are disposed in the axial direction coaxially and successively in the sequence “PS 2 , PS 3 ” on the first shaft section WS 1 of the two parallel shaft sections WS 1 , WS 2 .
  • a first spur gear ST 3 a of a third spur-gear stage STS 3 of the three spur-gear stages STS 2 , STS 3 , STS 4 , a first spur gear ST 4 a of the fourth spur-gear stage STS 4 , and a first spur gear ST 2 a of a second spur-gear stage STS 2 of the three spur-gear stages STS 2 , STS 3 , STS 4 , are disposed coaxially and successively on the first shaft section WS 1 upstream of the second planetary gear set PS 2 .
  • the result thereof is a sequence of “ST 3 a , ST 4 a , ST 2 a , PS 2 , PS 3 ”.
  • the drive shaft AN is disposed on the first shaft section WS 1
  • the output shaft AB is disposed on a second shaft section WS 2 of the two parallel shaft sections WS 1 , WS 2 .
  • the two shaft sections WS 1 , WS 2 are connected to one another via the three spur-gear stages STS 2 , STS 3 , STS 4 .
  • the shift elements K 1 , K 2 , K 3 , K 4 are designed as clutches, the two shift elements B 1 , B 2 are designed as brakes and are also referred to as such in the following.
  • Different transmission ratios between the drive shaft AN and the output shaft AB can be implemented by means of a selective engagement of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 . At least nine forward gears and at least one reverse gear can be implemented in this manner.
  • a coupling of the individual elements of the three planetary gear sets PS 1 , PS 2 , PS 3 to one another, to the three spur-gear stages STS 2 , STS 3 , STS 4 and to the drive shaft AN and to the output shaft AB is described in the following.
  • the planetary power-shift transmission 120 comprises at least nine connection elements, which are labeled 1 , 3 , 4 , 8 , 9 , 10 , 11 , 12 , 13 .
  • the connection elements 1 , 3 , 4 , 8 , 9 , 10 , 11 , 12 , 13 can be embodied as shafts, wherein shift elements, in particular clutches, can also be disposed within the connection elements 1 , 3 , 4 , 8 , 9 , 10 , 11 , 12 , 13 , as is described in more detail in the following.
  • a sun gear SO 2 of a second planetary gear set PS 2 of the three planetary gear sets PS 1 , PS 2 , PS 3 , and the drive shaft AN are connected to one another in a rotationally fixed manner and form a first connection element 1 .
  • a ring gear HO 3 of a third planetary gear set PS 3 of the three planetary gear sets PS 1 , PS 2 , PS 3 , and the carrier ST 2 of the second planetary gear set PS 2 are connected to one another in a rotationally fixed manner and form a third connection element 3 .
  • a ring gear HO 2 of the second planetary gear set PS 2 is connected to the first spur gear ST 2 a of the second spur-gear stage STS 2 .
  • a second spur gear ST 2 b of the second spur-gear stage STS 2 , and the output shaft AB are connected and form an eighth connection element 8 .
  • the fourth shift element K 4 is disposed in the eighth connection element 8 .
  • a first spur gear ST 4 a of the fourth spur-gear stage STS 4 is connected to the ring gear HO 2 of the second planetary gear set PS 2 .
  • the first spur gear ST 4 a of the fourth spur-gear stage STS 4 , the first spur gear ST 2 a of the second spur-gear stage STS 2 , and the ring gear HO 2 of the second planetary gear set PS 2 are connected to one another, thereby resulting in a fourth, a ninth, and a fourteenth connection element 4 , 9 , 14 .
  • Each of the connection elements 4 , 9 , 14 connects a common connection point to the first spur gear ST 4 a of the fourth spur-gear stage STS 4 , to the first spur gear ST 2 a of the second spur-gear stage STS 2 , and to the ring gear HO 2 of the second planetary gear set PS 2 , respectively.
  • the fourth connection element establishes a connection between the common connection point and the ring gear HO 2 of the second planetary gear set.
  • the ninth connection element establishes a connection between the common connection point and the first spur gear ST 4 a of the fourth spur-gear stage STS 4
  • the fourteenth connection element 14 establishes a connection between the common connection point and the first spur gear ST 2 a of the second spur-gear stage STS 2 .
  • the ring gear HO 1 of the first planetary gear set PS 1 is connected to the output shaft AB in a rotationally fixed manner and forms a tenth connection element 10 .
  • the carrier ST 1 of the first planetary gear set PS 1 is connected to the second spur gear ST 4 b of the fourth spur-gear stage STS 4 and forms an eleventh connection element 11 .
  • the sun gear SO 1 of the first planetary gear set PS 1 is connected to the second spur gear ST 3 b of the third spur-gear stage STS 3 and forms a twelfth connection element 12 .
  • the drive shaft AN is connected or coupleable to the first spur gear ST 3 a of the third spur-gear stage STS 3 via the first shift element K 1 , which is the clutch K 1 in this case, and forms a thirteenth connection element 13 .
  • the thirteenth connection element 13 comprises the first shift element K 1 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 , wherein the first shift element K 1 is disposed in the power flow between the drive shaft AN and the first spur gear ST 3 a of the third spur-gear set STS 3 .
  • a second shift element K 2 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the drive shaft AN and a carrier ST 3 of the third planetary gear set PS 3 .
  • a third shift element K 3 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the fourth connection element 4 of the ring gear HO 2 of the second planetary gear set PS 2 to the first spur gear ST 2 a of the second spur-gear stage STS 2 and the carrier ST 3 of the third planetary gear set PS 3 .
  • the eighth connection element 8 comprises a fourth shift element K 4 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 , wherein the fourth shift element K 4 is disposed in the power flow between the second spur gear ST 2 b of the second spur-gear stage STS 2 and the output shaft AB.
  • a fifth shift element B 1 —the brake B 1 in this case—of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the carrier ST 3 of the third planetary gear set PS 3 and a transmission housing GG.
  • a sixth shift element B 2 of the six shift elements K 1 , K 2 , K 3 , K 4 , B 1 , B 2 is disposed in the power flow between the sun gear SO 3 of the third planetary gear set PS 3 and the transmission housing GG.
  • FIGS. 9 to 11 show a gear pattern of the second main system having the first planetary gear set PS 1 on the output shaft AB.
  • FIG. 11 shows an alternative positioning of the first planetary gear set PS 1 on the output shaft AB.
  • FIG. 10 shows a schematic depiction of a further example embodiment of the second main system of the multi-stage transmission 120 , which was previously described with reference to FIG. 9 .
  • This is a variant interlocking of the multi-stage transmission 120 that is functionally identical to the second main system described with reference to FIG. 9 .
  • the gear pattern depicted in FIG. 10 corresponds to the gear pattern of a multi-stage transmission 120 depicted in FIG. 9 , from which a plurality of functionally identical, variant transmissions can be derived, wherein there are four additional, functionally identical, variant positions for the first shift element K 1 , i.e., the clutch K 1 , and one other variant position is possible for the fourth shift element K 4 , i.e., the clutch K 4 .
  • the four variant positions for the clutch K 1 are labeled A 5 , A 6 , A 7 , A 8 in FIG. 10
  • the variant position for the clutch K 4 is labeled A 4 .
  • the clutch K 1 is disposed in the twelfth connection element 12 between the second spur gear ST 3 b of the third spur-gear set STS 3 and the sun gear SO 1 of the first planetary gear set PS 1 .
  • the clutch K 1 is disposed in the tenth connection element 10 between the ring gear HO 1 of the first planetary gear set PS 1 and the output shaft AB.
  • the clutch K 1 is disposed in the eleventh connection element 11 between the second spur gear ST 4 b of the fourth spur-gear stage STS 4 and the carrier ST 1 of the first planetary gear set PS 1 .
  • the clutch K 1 is disposed in the ninth connection element between the first spur gear ST 4 a of the fourth spur-gear stage STS 4 and the common connection point of the fourth, ninth, and fourteenth connection elements.
  • One other variant position A 9 results for the clutch K 4 in addition to the variant position in the eighth connection element 8 between the output shaft AB and the second spur gear ST 2 b of the second spur-gear stage STS 2 .
  • the clutch K 4 is disposed in the fourteenth connection element 14 between the first spur gear ST 2 a of the second spur-gear stage STS 2 and the common connection point of the fourth, ninth, and fourteenth connection elements.
  • FIG. 10 shows one of the ten possible variant positions for the clutches K 1 , K 4 , in which each of the five variant positions for the clutch K 1 can be combined with the two variant positions for the clutch K 4 .
  • FIG. 10 therefore shows functionally identical, variant transmissions and gear patterns of the variant positions for the clutches K 1 , K 4 .
  • the first main systems having all planetary sets on the drive shaft AN which is shown in FIGS. 2 and 3 to 8
  • an entire series of variant transmissions is also possible in the case of the second main systems having one gear set on the output shaft AB.
  • These are largely identical to the variant transmissions of the first main system.
  • Other positions for the clutches K 1 , K 4 are possible here as well, in a manner analogous to the first main system, without the function of the transmission 120 being changed as a result.
  • These possible positions are depicted in FIG. 10 .
  • Four more possible positions (A 5 , A 6 , A 7 , A 8 ) result for the clutch K 1 , for example.
  • One more possible position (A 9 ) results for the clutch K 4 .
  • FIG. 11 shows a gear pattern of the multi-stage transmission 120 , as the second main system according to a further example embodiment of the present invention.
  • the first planetary gear set PS 1 is disposed on the output shaft AB.
  • the position of the planetary gear set PS 1 and the connection of the third and fourth spur-gear stages STS 3 , STS 4 has been varied. All transmission elements, connection elements, shafts, rotationally fixed connections, shift elements, and variant positions in the region of the first shaft section WS 1 are identical to the example embodiment shown in FIG. 10 .
  • the eighth and tenth connection elements 8 , 10 on the second shaft section WS 2 correspond to the example embodiment shown in FIG. 10 .
  • the eleventh and twelfth connection elements 11 , 12 have been changed as compared to the example embodiment shown in FIG. 10 .
  • the eleventh connection element 11 connects the sun gear SO 1 of the first planetary gear set PS 1 to the second spur gear ST 4 a of the fourth spur-gear stage STS 4 .
  • the clutch K 1 is disposed in the region of the eleventh connection element 11 .
  • the twelfth connection element 12 connects the second spur gear ST 3 b of the third spur-gear stage STS 3 to the ring gear HO 1 of the third planetary gear set PS 1 .
  • the clutch K 1 is disposed in the region of the twelfth connection element 12 .
  • FIGS. 12 and 13 show a hybridization of a multi-stage transmission according to the invention.
  • an electric machine or any other type of force/power source can be disposed on each shaft of a multi-stage transmission according to any one of the example embodiments described.
  • FIG. 12 shows a schematic depiction of a power-shiftable multi-stage transmission 120 , which is designed as a first main system and comprises a power source EM according to one example embodiment of the present invention.
  • the power source EM is designed as an electric machine EM. Therefore, this is a hybridization with an electric machine EM, which acts directly on the drive shaft AN of the multi-stage transmission 120 , which is described with reference to FIG. 2 and is designed as a first main system.
  • the multi-stage transmission 120 known from FIG. 2 additionally comprises an electric machine EM and an additional clutch K 0 on the drive shaft AN.
  • the electric machine EM as the load source
  • the clutch K 0 are additionally disposed between an internal combustion engine, which drives the drive shaft AN and which is shown in FIG. 1 , for example, and the electric machine EM.
  • the clutch K 0 , the electric machine EM, the two spur-gear stages STS 1 , STS 2 , and the three planetary gear sets PS 1 , PS 2 , PS 3 are disposed coaxially and successively on the first shaft section WS 1 in the axial direction in the sequence “K 0 , EM, PS 1 , STS 1 , STS 2 , PS 2 , PS 3 ”.
  • the electric machine acts directly on the drive shaft.
  • the hybridization is possible with all the example embodiments described and shown in FIGS. 1 to 11 .
  • the connection of the electric machine EM to the drive shaft AN is a variant embodiment presented as an example, wherein, in principle, an electric machine or any other source of force or power can be disposed on each shaft of a planetary power-shift transmission according to the invention.
  • the additional clutch K 0 in addition to the electric machine EM, is placed between an internal combustion engine as shown in FIG. 1 , for example, and the electric machine EM, as shown in FIG. 12 , it is possible to drive all gears—as described with reference to FIG. 3 , for example—both forward and in reverse, exclusively electrically. To this end, the internal combustion engine is decoupled by the disengaged clutch K 0 .
  • FIG. 13 shows a schematic depiction of a power-shiftable multi-stage transmission 120 comprising a power source EM, according to one example embodiment of the present invention.
  • the power source EM is designed as an electric machine EM, similarly to the example embodiment described with reference to FIG. 12 . Therefore, this is a hybridization with an electric machine EM, which is disposed axially parallel to the drive shaft AN of the example embodiment of a multi-stage transmission 120 described with reference to FIG. 6 .
  • the electric machine EM is not directly connected to the first connection element in a rotationally fixed manner, but rather is coupled to the first connection element via a fifth spur-gear stage STS 5 .
  • the electric machine EM is disposed axially parallel to the shaft sections, on the side of the first shaft section opposite the second shaft section.
  • the arrangement of the planetary gear sets PS 1 , PS 2 , PS 3 and the spur-gear stages STS 1 , STS 2 , and the connections or mutual interlockings correspond to the example embodiment of the present invention shown in FIG. 6 .
  • the example embodiments described and shown in the figures are selected merely as examples. Different example embodiments can be combined with one another in entirety or in terms of individual features. It is also possible to add features of one example embodiment to another example embodiment. If an example embodiment has an “and/or” statement between a first feature and a second feature, this is intended to mean that the example embodiment according to one embodiment has both the first feature and the second feature and, according to a further embodiment, has either only the first feature or only the second feature.
  • the planetary sets and the shift elements can have other spatial positions per se and with respect to one another that do not affect the function of the described transmission.
  • gear increments can result for all the example embodiments of the transmission family depicted and described, using the same gear pattern and depending on the stationary transmission ratio of the individual planetary sets, thereby making it possible to obtain an application-specific or vehicle-specific variation.
  • additional freewheels at each suitable location in the multi-staged transmission, for example, between a shaft and the housing, or possibly to connect two shafts.
  • an axle differential and/or a distributor differential can be disposed on the drive side or on the output side.
  • the multi-stage transmission according to the invention can be advantageously developed accordingly, for example, by disposing a torsional-vibration damper between the drive motor and the transmission.
  • the drive shaft AN can be separated from a drive motor, as needed, by a clutch element, wherein a hydrodynamic converter, a hydraulic clutch, a dry start-up clutch, a wet start-up clutch, a magnetic powder clutch, or a centrifugal clutch can be used as the clutch element. It is also possible to dispose such a start-up element in the power flow direction downstream of the transmission wherein, in this case, the drive shaft AN is permanently connected to the crankshaft of the drive motor.
  • a wear-free brake such as a hydraulic or electric retarder, for example, on each shaft, preferably on the drive shaft AN or the output shaft AB, which is of special significance for use in commercial vehicles in particular.
  • a power take-off drive can be provided on each shaft, preferably on the drive shaft AN or the output shaft AB, for driving additional assemblies.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
US14/396,092 2012-04-27 2013-03-13 Multi-stage power-shift transmission Expired - Fee Related US9506531B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102012207099.0 2012-04-27
DE102012207099 2012-04-27
DE102012207099.0A DE102012207099B4 (de) 2012-04-27 2012-04-27 Lastschaltbares Mehrstufengetriebe
PCT/EP2013/055063 WO2013159994A1 (de) 2012-04-27 2013-03-13 Lastschaltbares mehrstufengetriebe

Publications (2)

Publication Number Publication Date
US20150080164A1 US20150080164A1 (en) 2015-03-19
US9506531B2 true US9506531B2 (en) 2016-11-29

Family

ID=47882149

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/396,092 Expired - Fee Related US9506531B2 (en) 2012-04-27 2013-03-13 Multi-stage power-shift transmission

Country Status (5)

Country Link
US (1) US9506531B2 (zh)
EP (1) EP2841800B1 (zh)
CN (1) CN104254711B (zh)
DE (1) DE102012207099B4 (zh)
WO (1) WO2013159994A1 (zh)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10533643B2 (en) 2017-03-20 2020-01-14 Zf Friedrichshafen Ag Vehicle transmission
US10875518B2 (en) * 2017-03-24 2020-12-29 Bayerische Motoren Werke Aktiengesellschaft Combined multistage hybrid transmission and powertrain comprising same

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015223274A1 (de) * 2015-11-25 2017-06-01 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug, sowie Antriebsstrang für ein Kraftfahrzeug mit einem solchen Getriebe

Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2065400A1 (de) 1970-04-30 1973-08-09 Nissan Motor Planetenwechselgetriebe mit mindestens drei saetzen
US5358458A (en) 1990-08-15 1994-10-25 Massey-Ferguson Services, N.V. Planetary gear units
DE10115985A1 (de) 2001-03-30 2002-10-10 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
US20060142111A1 (en) 2004-12-24 2006-06-29 Park Dong H Powertrain of an automatic transmission
US20090036252A1 (en) 2007-07-31 2009-02-05 Gm Global Technology Operations, Inc. Nine speed automatic transmission
US20100035718A1 (en) 2008-08-07 2010-02-11 Honda Motor Co., Ltd. Automatic transmission
US7819772B2 (en) 2007-03-23 2010-10-26 EGS Entwicklungsgesellschaft fuer Getriebesysteme mbH Powershiftable multistage transmission
DE102010019649A1 (de) 2009-05-11 2011-01-05 GM Global Technology Operations, Inc., Detroit Acht-, Neun- und Zehngang-Automatikgetriebe
DE102009018958A1 (de) 2009-04-25 2011-02-10 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Mehrstufengetriebe
US20110045941A1 (en) * 2009-08-20 2011-02-24 Zf Friedrichshafen Ag Multi step transmission
US20120053003A1 (en) 2010-09-01 2012-03-01 Hyundai Motor Company Gear train of automatic transmission for vehicles
US20120088626A1 (en) * 2010-10-11 2012-04-12 Gm Global Technology Operations, Inc. Multi-speed transmission with external drive gearsets
US20120088627A1 (en) 2010-10-11 2012-04-12 Gm Global Technology Operations, Inc. Multi-speed transmission with external drive gearsets
US20120094799A1 (en) 2010-10-13 2012-04-19 Gm Global Technology Operations, Inc. Multi-speed transmission with external drive gearsets
DE102011080566A1 (de) 2011-08-08 2013-02-14 Zf Friedrichshafen Ag Lastschaltbares Mehrstufengetriebe
US20150087469A1 (en) * 2012-04-27 2015-03-26 Zf Friedrichshafen Ag Multi-stage power-shift transmission
US20150126324A1 (en) * 2012-06-26 2015-05-07 Zf Friedrichshafen Ag Multi-Stage Power-Shift Transmission

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101265958B (zh) * 2007-06-07 2010-11-17 黄庆培 多级变速器
US8016709B2 (en) * 2009-01-09 2011-09-13 GM Global Technology Operations LLC Multi-speed transmission having three planetary gear sets

Patent Citations (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2065400A1 (de) 1970-04-30 1973-08-09 Nissan Motor Planetenwechselgetriebe mit mindestens drei saetzen
US5358458A (en) 1990-08-15 1994-10-25 Massey-Ferguson Services, N.V. Planetary gear units
DE69106861T2 (de) 1990-08-15 1995-06-08 Massey Ferguson Sa Planeten-getriebeeinheit.
DE10115985A1 (de) 2001-03-30 2002-10-10 Zahnradfabrik Friedrichshafen Mehrstufengetriebe
US20040147358A1 (en) * 2001-03-30 2004-07-29 Eberhard Biermann Multi-stage gearbox
US6984187B2 (en) 2001-03-30 2006-01-10 Zf Friedrichshafen Ag Multi-stage gearbox
US20060142111A1 (en) 2004-12-24 2006-06-29 Park Dong H Powertrain of an automatic transmission
DE102005018804A1 (de) 2004-12-24 2006-07-13 Dong Hoon Park Antriebsstrang eines Automatikgetriebes
US7819772B2 (en) 2007-03-23 2010-10-26 EGS Entwicklungsgesellschaft fuer Getriebesysteme mbH Powershiftable multistage transmission
US20090036252A1 (en) 2007-07-31 2009-02-05 Gm Global Technology Operations, Inc. Nine speed automatic transmission
US8388488B2 (en) 2007-10-12 2013-03-05 GM Global Technology Operations LLC Eight, nine and ten speed automatic transmissions
US20100035718A1 (en) 2008-08-07 2010-02-11 Honda Motor Co., Ltd. Automatic transmission
DE102009018958A1 (de) 2009-04-25 2011-02-10 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Mehrstufengetriebe
DE102010019649A1 (de) 2009-05-11 2011-01-05 GM Global Technology Operations, Inc., Detroit Acht-, Neun- und Zehngang-Automatikgetriebe
US20110045941A1 (en) * 2009-08-20 2011-02-24 Zf Friedrichshafen Ag Multi step transmission
US20120053003A1 (en) 2010-09-01 2012-03-01 Hyundai Motor Company Gear train of automatic transmission for vehicles
US20120088626A1 (en) * 2010-10-11 2012-04-12 Gm Global Technology Operations, Inc. Multi-speed transmission with external drive gearsets
US20120088627A1 (en) 2010-10-11 2012-04-12 Gm Global Technology Operations, Inc. Multi-speed transmission with external drive gearsets
US20120094799A1 (en) 2010-10-13 2012-04-19 Gm Global Technology Operations, Inc. Multi-speed transmission with external drive gearsets
DE102011080566A1 (de) 2011-08-08 2013-02-14 Zf Friedrichshafen Ag Lastschaltbares Mehrstufengetriebe
US20150087469A1 (en) * 2012-04-27 2015-03-26 Zf Friedrichshafen Ag Multi-stage power-shift transmission
US20150126324A1 (en) * 2012-06-26 2015-05-07 Zf Friedrichshafen Ag Multi-Stage Power-Shift Transmission

Non-Patent Citations (5)

* Cited by examiner, † Cited by third party
Title
German Search Report Corresponding to 10 2012 207 028.1 mailed Mar. 28, 2014.
German Search Report Corresponding to 10 2012 207 099.0 mailed Jul. 10, 2014.
International Search Report Corresponding to PCT/EP2013/055063 mailed Jul. 23, 2013.
International Search Report Corresponding to PCT/EP2013/055065 mailed Jun. 26, 2013.
Written Opinion Corresponding to PCT/EP2013/055063 mailed Jul. 23, 2013.

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10533643B2 (en) 2017-03-20 2020-01-14 Zf Friedrichshafen Ag Vehicle transmission
US10875518B2 (en) * 2017-03-24 2020-12-29 Bayerische Motoren Werke Aktiengesellschaft Combined multistage hybrid transmission and powertrain comprising same

Also Published As

Publication number Publication date
DE102012207099A1 (de) 2013-10-31
CN104254711A (zh) 2014-12-31
EP2841800B1 (de) 2018-10-03
WO2013159994A1 (de) 2013-10-31
US20150080164A1 (en) 2015-03-19
EP2841800A1 (de) 2015-03-04
DE102012207099B4 (de) 2020-11-19
CN104254711B (zh) 2017-11-10

Similar Documents

Publication Publication Date Title
US9810299B2 (en) Multi-stage power-shift transmission
US9599195B2 (en) Multi-speed gearbox
US9039562B2 (en) Multi-speed gearbox
US8894536B2 (en) Multistep gear mechanism
US8944953B2 (en) Multistep gear mechanism
US8727929B2 (en) Multistep gear mechanism of planetary design
US8663056B2 (en) Multi-ratio transmission
US8444525B2 (en) Multi-ratio transmission
US9482318B2 (en) Multi-speed gearbox
US10378616B2 (en) Transmission for a vehicle
US9234569B2 (en) Multi-speed gearbox
US20110045936A1 (en) Multi step transmission
US9267576B2 (en) Multi-speed gearbox
US9175752B2 (en) Multi-speed gearbox
US9360086B2 (en) Multi-speed gearbox
US9273768B2 (en) Multi-stage power-shift transmission
US9011288B2 (en) Multi-ratio transmission
US9188199B2 (en) Multi-ratio transmission
US20150184723A1 (en) Multi-Speed Gearbox
US9518635B2 (en) Multi-speed transmission
US9347526B2 (en) Multi-ratio transmission
US9127756B2 (en) Multi-ratio transmission
US9022895B2 (en) Multi-ratio transmission
US9366320B2 (en) Multi-speed gearbox
US9506531B2 (en) Multi-stage power-shift transmission

Legal Events

Date Code Title Description
AS Assignment

Owner name: ZF FRIEDRICHSHAFEN AG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BECK, STEFAN;REEL/FRAME:034002/0814

Effective date: 20140724

FEPP Fee payment procedure

Free format text: PAYOR NUMBER ASSIGNED (ORIGINAL EVENT CODE: ASPN); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

STCF Information on status: patent grant

Free format text: PATENTED CASE

FEPP Fee payment procedure

Free format text: MAINTENANCE FEE REMINDER MAILED (ORIGINAL EVENT CODE: REM.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

LAPS Lapse for failure to pay maintenance fees

Free format text: PATENT EXPIRED FOR FAILURE TO PAY MAINTENANCE FEES (ORIGINAL EVENT CODE: EXP.); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

STCH Information on status: patent discontinuation

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

FP Lapsed due to failure to pay maintenance fee

Effective date: 20201129